EP0486941B1 - Compensateur pour conduites ou similaires - Google Patents

Compensateur pour conduites ou similaires Download PDF

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Publication number
EP0486941B1
EP0486941B1 EP91119409A EP91119409A EP0486941B1 EP 0486941 B1 EP0486941 B1 EP 0486941B1 EP 91119409 A EP91119409 A EP 91119409A EP 91119409 A EP91119409 A EP 91119409A EP 0486941 B1 EP0486941 B1 EP 0486941B1
Authority
EP
European Patent Office
Prior art keywords
piston
sleeve
sealing
core
compensator according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP91119409A
Other languages
German (de)
English (en)
Other versions
EP0486941A1 (fr
Inventor
Jürgen Bläss
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Friatec AG
Original Assignee
Friatec AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Friatec AG filed Critical Friatec AG
Publication of EP0486941A1 publication Critical patent/EP0486941A1/fr
Application granted granted Critical
Publication of EP0486941B1 publication Critical patent/EP0486941B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L27/00—Adjustable joints; Joints allowing movement
    • F16L27/12—Adjustable joints; Joints allowing movement allowing substantial longitudinal adjustment or movement
    • F16L27/127—Adjustable joints; Joints allowing movement allowing substantial longitudinal adjustment or movement with means for locking the longitudinal adjustment or movement in the final mounted position
    • F16L27/1275—Adjustable joints; Joints allowing movement allowing substantial longitudinal adjustment or movement with means for locking the longitudinal adjustment or movement in the final mounted position by means of at least an external threaded bolt
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L27/00—Adjustable joints; Joints allowing movement
    • F16L27/12—Adjustable joints; Joints allowing movement allowing substantial longitudinal adjustment or movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L47/00—Connecting arrangements or other fittings specially adapted to be made of plastics or to be used with pipes made of plastics
    • F16L47/18—Adjustable joints; Joints allowing movement

Definitions

  • a metal compensator for metallic pressure pipelines is known, which is intended in particular for hydraulic fluids.
  • the compensator contains a ball joint and additional connecting parts for the pipeline to absorb rotary movements.
  • the compensator is surrounded by a flexible sleeve to prevent hydraulic fluid from escaping. Due to the differently large temperature coefficients of plastic on the one hand and metal on the other hand, such a compensator in plastic pipelines can only be used together with special transition pieces from plastic to metal, which would increase the overall length accordingly.
  • Plastic pipelines especially chlorinated polyvinyl chloride or polyethylene, are increasingly used in installation technology for water supply in buildings. Due to the increased temperature coefficient of plastic pipes compared to metal pipes, special measures to compensate for changes in length due to temperature changes in the water carried in the pipe, particularly in the case of hot water supply in the form of fresh water or heating water, are just as necessary as due to temperature changes in the environment. Up to now, fixed points and expansion bends had to be arranged very carefully when laying plastic pipelines, which required considerable installation effort. Furthermore, rubber compensators with flexible parts made of an elastomeric material or special expansion sleeves were often used for longitudinal compensation. Assembly must be carried out with particular care so that the changes in length of the pipeline to be expected during operation can be absorbed.
  • the object of the invention is to further develop a compensator of the type mentioned, in particular for use in pressure pipelines, in such a way that a high level of operational reliability is ensured for a long time and a small construction volume is achieved with little manufacturing effort.
  • the wall thickness of the radially inner plastic sleeve can be made comparatively small; this is favorable in terms of the outside diameter as well as in terms of the required use of material and weight.
  • the core has an inside diameter which is essentially the same size as the inside diameter of the pipe of the pipeline to be connected.
  • Cross-sectional changes, in particular cross-sectional reductions, which are very fluid are unfavorable, are avoided as well as vortex formation and the resulting flow noise.
  • the piston in the pipe ends to be connected is expediently provided with the same diameter in the following area as the pipe inner diameter.
  • the movable piston has a flange, the rear wall of which is connected to the interior of the pipeline via at least one through opening.
  • the rear wall is part of an annular chamber in which the pressure prevailing in the pipeline is present.
  • An axial force acts on the movable piston via the rear wall, which is directed against the tensile force as a result of the pressure or pressure surges inside the pipeline.
  • the area of the rear wall is specified in such a way that an equilibrium with the axial tensile force is achieved even taking friction forces into account.
  • the area of the rear wall is at least equal to or larger than the inner area of the movable piston.
  • a sleeve which is firmly connected to the core surrounds it and the movable piston, the flange of which can be moved along the inner surface of the sleeve, sealing of said chamber being achieved by means of sealing rings.
  • the stroke of the piston can easily be set very large.
  • the compensator contains a core 2, a piston 4 and a sleeve 6.
  • the core 2 and the sleeve 6 are firmly connected to one another to form an annular chamber 8, in which the piston 4 in the direction of a longitudinal axis 10 is arranged axially displaceable relative to those.
  • the core 2 and the piston 4 each contain a sleeve 12, 14 at the axial ends of the compensator, in which ends of pipes 13, 15 of the pipeline, shown in broken lines here, in particular via Adhesive connections are tight and firmly connectable.
  • the sleeves 12, 14 form the connection elements for the pipeline integrated in the core 2 or the piston 4, a direct connection being achieved in the shortest possible way, with a short overall length and without additional components.
  • connection elements essentially within the core 2 and / or the piston 4 proves to be particularly advantageous with regard to the construction volume and in particular the construction length of the compensator.
  • a screw connection can alternatively also be formed in the sleeves 12, 14 for the direct connection of the pipes 13, 15.
  • other connecting devices and elements can also be provided at the axial ends of the core 2 or the piston 4 within the scope of this invention.
  • the length of the annular chamber 8 in the direction of the longitudinal axis 10 and thus the stroke of the piston 4 is predetermined in accordance with the expected changes in length of the pipeline, a large stroke being reliably made possible.
  • the stroke is larger by a factor than the nominal width of the pipeline, this factor having at least the value 2.
  • the sleeves 12, 14 extend axially inwards up to an annular collar 17, 19. These annular collars 17, 19 form stops when the tubes 13, 15 are inserted.
  • the annular collar 19 of the sleeve 14 prevents the tube 15 from being too wide is introduced, whereby the free mobility and ultimately the function of the compensator would be at least considerably restricted.
  • the coils have a height which, within the scope of this invention, is essentially the same size as the wall thickness of the tubes 13, 15. This is very favorable with regard to the flow of the medium in the compensator being as swirl-free as possible.
  • the core 2, the piston 4 and the sleeve 6 are the medium flowing through the pipeline, in particular under pressure standing water, exposed and are conveniently manufactured by injection molding.
  • the sleeve 6 is surrounded radially on the outside by a jacket 16, which consists of metal, in particular aluminum.
  • the jacket 16 reliably absorbs the compressive forces and the sleeve 6 made of plastic can be made comparatively thin-walled; without the jacket 16, the sleeve 6 would have to have a considerable wall thickness, which on the one hand would make the outer diameter of the compensator unbearably large and, apart from manufacturing difficulties, the total weight of the compensator would be considerably greater in the case of a thick-walled design.
  • the sleeve 6 has a radial recess on the inside with an annular shoulder 18, with respect to which a ring 20 of the core 2 is aligned and fastened in a defined manner.
  • the ring shoulder 18 serves as a stop during the assembly and the preferred gluing of the core 2 with the sleeve 6.
  • the ring 20 is arranged in the area of the sleeve 12 via a radial web 22, which has a vent hole 24, and as an integral part of the core 2 educated.
  • the piston 4 contains in the area of the annular chamber 8 a radially outwardly pointing, annular extension or flange 26 which, on the one hand, bears against the outer surface 28 of the core 2 and, on the other hand, against the inner surface 30 with sufficient play to enable an axial relative movement to be largely unimpeded .
  • the sleeve 6 contains a radially inwardly directed extension 32, which in turn rests on the outer surface 34 of the piston 4 with a corresponding clearance.
  • a total of three sealing rings 36, 37, 38 are provided in the flange 26 and in the shoulder 32, which ensure a reliable seal between the mutually movable surfaces.
  • annular chamber 40 Between the radially outward flange 26 and the radially inward extension 32 there is an annular chamber 40, the axial length of which is predefined in accordance with the respective position of the piston 4 relative to the core 2 and the sleeve 6 is. It is essential that there is a connection between the chamber 40 and the interior 42 acted upon by the medium.
  • the piston 4 has at least one continuous radial bore 44 and a connecting groove 46 in the region of the inner surface.
  • a plurality of such bores and connecting grooves are expediently provided distributed over the circumference, a second connecting groove 47 being recognizable here.
  • Several connecting grooves increase safety with regard to the risk of clogging due to contamination.
  • the radial depth of the individual connecting grooves can be specified to be correspondingly small, so that the radial wall thickness of the piston 4 can also be kept small.
  • the annular surface of the rear wall 48 is at least the same, expediently greater by the frictional forces of the seals than the cross-sectional area 50 in the interior of the piston 4.
  • a pressure or pressure surge effective in the pipeline basically results a force component such that the piston 4 is pulled away from the core 2 in the direction of arrow 52. Since the pressure is also effective in the chamber 40 according to the invention, an opposing force component acts on the rear wall 48. Since the ring surface of the rear wall 48 is essentially the same size as the cross-sectional area 50, a balance of forces is established and a relative movement in the direction of the arrow 52 is prevented.
  • the already mentioned sealing rings 36 to 38 are arranged in ring grooves 56, 57, 58 of the piston 4 or the sleeve 6.
  • the two annular grooves 56, 57 of the piston 4 are connected to one another by a radial through bore 60, into which an axial bore 62 opens.
  • This axial bore 62 is closed at the free end of the piston 4 by means of a knurled screw 64 and a sealing ring 66.
  • the sealing rings 36, 37 are designed in such a way that, when properly functioning, no liquid can escape from the interior 42 or the chamber 40 to the outside.
  • a radial bore 68 opens into the annular groove 58 with the sealing ring 38 on the side facing away from the pressure, which is closed again with a small screw 70 and a sealing ring 72 or can be opened for leak monitoring.
  • the sealing ring 38 is shown greatly enlarged, namely the left part according to FIG. 1 near the screw for leak monitoring.
  • the sealing ring 38 contains three sealing lips 74 to 76 which bear on the outer surface of the piston under elastic prestress. These sealing lips are inclined at an angle 80 with respect to the radial plane 78 in the direction of the chamber or pressure side.
  • the pressure acting from the chamber in the direction of arrow 82 causes the closest sealing lip 74 to be pressed against the outer surface of the piston.
  • the sealing lips 75 and 76 are only minimally stressed in the initial stage after installation when the piston moves and are therefore subject to practically no wear.
  • the angle 80 is expediently of the order of 45 °.
  • annular chambers 84 to 86 are present in front of the sealing lips 74 to 76, liquid initially only being able to get into the first chamber 84 and the pressure effective there pressing the sealing lip 74 against the outer wall of the piston. If after a long time the sealing effect deteriorates as a result of wear, liquid also enters the next chamber 85, so that the second sealing lip 75 now ensures the seal to the outside.
  • At least one radial opening 88 which communicates with the bore 68 of the sleeve 6 shown in FIG. 1, opens into the third annular chamber 86. For security reasons, at least two, preferably four such openings are expediently arranged distributed over the circumference.
  • the sealing ring 38 has, on the side facing the bottom of the annular groove, a number, here seven, annular beads 90, which enable reliable installation and compensation of manufacturing tolerances of the annular groove and also result in material savings.
  • the width 92 of the sealing lips measured perpendicular to the direction of inclination is essentially the same as the thickness 94 of the sealing ring between the bottom 96 and the outer surface 98.
  • the distance 100 between the sealing lips, which is also orthogonal to the direction of inclination, and thus the width of the annular chamber is likewise essentially the same as the width 92 and / or the thickness 94.
  • the total radial thickness 102 between the outer surface 98 and the inner edge of the unloaded sealing lip is essentially the same size as the axial distance 104 between adjacent sealing lips.
  • the overall axial length 106 of the sealing ring is substantially greater than the distance 104 between two adjacent sealing lips by a factor corresponding to that of the sealing lips.
  • the distance 104 is a factor between 2 and 3 greater than the width 92 and / or the thickness 94.
  • the total thickness 102 is very small, so that the injection molded parts, namely flange 26, the shoulder 32 and the piston 4 and the core 2 can have small wall thicknesses in the area of the respective sealing ring.
  • the sealing ring 37 of the piston 4 shown with reference to FIG. 1 is designed essentially in accordance with the sealing ring 38 of the sleeve 6 explained above. Apart from the fact that in the sealing ring 36 of the piston 4 the sealing lips are directed radially outward, the sealing ring 36 also has the same structure and mode of operation as the sealing ring 38 explained above.
  • the radial openings of the sealing rings 36, 37 lie essentially in the same radial plane as the radial through bore 60 between the two chambers.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Sealing Devices (AREA)
  • Liquid Crystal (AREA)
  • Load-Engaging Elements For Cranes (AREA)
  • Lubricants (AREA)

Claims (12)

  1. Compensateur destiné à absorber des variations de longueur dans une canalisation, qui comprend des tuyaux (13, 15) en matière plastique et qui conduit des liquides sous pression, comprenant un noyau (2) et un piston (4) qui sont fait de matière plastique et sont raccordés chacun à l'un des tuyaux (13, 15) et peuvent se déplacer l'un par rapport à l'autre dans la direction axiale, une chambre annulaire (8) située entre le noyau (2) et une douille (6) réunie à ce noyau et faite de matière plastique, chambre dans laquelle le piston (4) peut se déplacer axialement, au moins sur une longueur partielle, une chambre (40) pouvant être chargée par la pression de la canalisation étant ménagée entre le piston (4) et la douille (6) et des éléments de raccordement pour les tuyaux (15) étant intégrés dans le noyau (2) et dans le piston (4) et constitué en particulier par des manchons (12, 14),
    caractérisé en ce que la douille (6) est entourée extérieurement d'une gaine (16) en métal.
  2. Compensateur selon la Revendication 1, caractérisé en ce que la douille (6) présente une saillie (32) dirigée radialement vers l'intérieur et munie d'une bague d'étanchéité (38) qui s'appuie à joint étanche contre une surface extérieure (34) du piston (4), la chambre (40) étant située dans la direction axiale entre la saillie (32) et une paroi arrière (48) d'une collerette (26) du piston (4).
  3. Compensateur selon la Revendication 2, caractérisé en ce que l'aire de la paroi arrière (48) est sensiblement égale à l'aire de section libre (50) du piston (4), ou, de préférence, supérieure à cette aire dans une mesure qui correspond aux forces de frottement des bagues d'étanchéité (36 à 38), l'aire de section (50) citée étant formée par l'aire interne du piston (4) qui entoure le noyau (2).
  4. Compensateur selon l'une des Revendications 1 à 3, caractérisé en ce que le piston (4) présente sur sa surface interne au moins une rainure de communication (46, 47) qui débouche de préférence dans la chambre (40), par l'intermédiaire d'un perçage (44), notamment radial, et/ou en ce que le perçage (44) est prévu sensiblement dans la région de la paroi arrière (48) de la collerette (26).
  5. Compensateur selon l'une des Revendications 1 à 4, caractérisé en ce que les éléments de raccordement, notamment formés de manchons (12, 14) présentent des embases annulaires (17, 19) à l'intérieur du noyau (2) et/ou du piston (4) et/ou en ce que l'épaisseur radiale des embases annulaires (17, 19) est sensiblement égale à l'épaisseur de paroi des tuyaux (13, 15).
  6. Compensateur selon l'une des Revendications 1 à 5, caractérisé en ce que la douille (6) présente la saillie (32) à l'une de ses extrémités axiales, cette saillie étant de préférence appuyée contre un fond (54) de la gaine (16) et/ou en ce que la douille (6) présente, à l'autre extrémité, un épaulement annulaire (18) servant à assurer l'alignement défini et la fixation, notamment par collage, du noyau (2).
  7. Compensateur selon une des Revendications 1 à 6, caractérisé en ce que le noyau (2) présente, notamment dans la région d'un manchon (12) recevant la canalisation, un voile radial (22) et/ou une bague (20) par l'intermédiaire desquels s'effectue le raccordement et/ou la fixation à la douille (6).
  8. Compensateur selon l'une des Revendications 1 à 7, caractérisé en ce que , pour l'étanchéité de la chambre (40), des bagues d'étanchéité (36 à 38) sont prévues, en particulier dans des gorges annulaires (56 à 58) du piston (4) et/ou de la douille (6) et/ou en ce que ces bagues d'étanchéité (36 à 38) présentent au moins une chambre annulaire (86) située en aval d'une lèvre d'étanchéité (74) dans le sens de la pression, cette chambre ou ces chambres permettant de réaliser une surveillance des fuites par l'intermédiaire d'au moins une percée (88) et/ou d'un perçage (60, 62, 68).
  9. Compensateur selon la revendication 8, caractérisé en ce que la bague d'étanchéité présente une autre lèvre d'étanchéité (76) en aval de la chambre annulaire (86) précitée, dans le sens de la pression et/ou en ce que la bague d'étanchéité (38) présente au moins deux lèvres d'étanchéité (74, 75) en amont de la chambre annulaire (86) dans le sens de la pression et/ou en ce que les bagues d'étanchéité (36 à 38) comprennent au moins une percée (88) qui est en communication, d'une part avec la chambre annulaire (86) et, d'autre part, avec un évidement ou perçage (60, 62, 68) du piston (4) ou de la douille (6) respectivement, qui peut être obturé de l'extérieur.
  10. Compensateur selon l'une des Revendications 1 à 9, caractérisé en ce que les au moins deux, de préférence trois, lèvres d'étanchéité (74 76) sont inclinées d'un angle (80) sur le plan radial (78) vers le côté sur lequel la pression agit, cet angle étant avantageusement d'entrée 40⁻ et 50⁻, de préférence sensiblement égal à 45°.
  11. Compensateur selon l'une des Revendications 1 à 10, caractérisé en ce que la largeur (92) mesurée perpendiculairement à la direction d'inclinaison de chaque lèvre d'étanchéité (74 à 76) est sensiblement égale à la distance (100), elle aussi mesurée perpendiculairement à la direction d'inclinaison, entre les lèvres d'étanchéité adjacentes.
  12. Compensateur selon l'une des Revendications 1 à 11, caractérisé en ce que l'épaisseur radiale (94) de la bague d'étanchéité est sensiblement égale à la largeur précitée (92) et/ou à la distance (100) entre les lèvres d'étanchéité (74 à 76) et/ou en ce que l'épaisseur totale radiale (102) mesurée entre la surface externe (98) et la pointe de la lèvre d'étanchéité à l'état déchargé est supérieure à la largeur radiale (94) d'un facteur d'entre 2 et 3.
EP91119409A 1990-11-23 1991-11-14 Compensateur pour conduites ou similaires Expired - Lifetime EP0486941B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4037279A DE4037279C2 (de) 1990-11-23 1990-11-23 Kompensator
DE4037279 1990-11-23

Publications (2)

Publication Number Publication Date
EP0486941A1 EP0486941A1 (fr) 1992-05-27
EP0486941B1 true EP0486941B1 (fr) 1994-10-12

Family

ID=6418787

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91119409A Expired - Lifetime EP0486941B1 (fr) 1990-11-23 1991-11-14 Compensateur pour conduites ou similaires

Country Status (4)

Country Link
EP (1) EP0486941B1 (fr)
AT (1) ATE112834T1 (fr)
DE (2) DE4037279C2 (fr)
DK (1) DK0486941T3 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4424921A1 (de) * 1994-07-14 1996-01-18 Rafeld Kunststofftechnik Gmbh Kompensator für Rohrleitungen

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE550676A (fr) *
DE688624C (de) * 1937-09-11 1940-02-26 Adolf Winterhoff Dichtungsring fuer Kolben, insbesondere fuer Kolbenpumpen, von im Querschnitt W-foermigem Profil
DE711737C (de) * 1938-04-02 1941-10-06 Kupfer Asbest Co Einbaufertige gehaeuselose Wellendichtung zur Abdichtung gegen zersetzende Fluessigkeiten und Gase
US3427051A (en) * 1967-02-24 1969-02-11 Gen Dynamics Corp Fluid pressure coupling
BE712655A (fr) * 1967-03-29 1968-07-31
US3695634A (en) * 1970-10-19 1972-10-03 Hydro Tech Services Inc Adjustable length coupling
GB1405410A (en) * 1971-12-29 1975-09-10 Horne Eng Co Ltd Seal for use in control system positioning devices
DE2308820C3 (de) * 1973-02-22 1984-09-20 Gelenkwellenbau Gmbh, 4300 Essen Axial bewegliche Lippendichtung für die Keilwellennabe einer Gelenkwelle
US4687232A (en) * 1985-12-27 1987-08-18 Zimmerman Harry M Pipe slip joint system

Also Published As

Publication number Publication date
ATE112834T1 (de) 1994-10-15
DE4037279C2 (de) 1994-06-30
EP0486941A1 (fr) 1992-05-27
DK0486941T3 (da) 1994-11-14
DE59103227D1 (de) 1994-11-17
DE4037279A1 (de) 1992-05-27

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